Governor device



March 6, 1956 R. H. THORNER GOVERNOR DEVICE 4 Sheets-Sheet 1 Filed March 21, 1951 INVEN TOR. Poeser H. 7740mm? nesora 5. ATTDRNfiK March 6, 1956 H, THORNER 2,737,165

GOVERNOR DEVICE Filed March 21, 1951 4 Shqets-Sheet 3 INVENTOR. PC5527 H. 774o/2M5R QK W A TTORIVEY March 1956i R. H. THORNER 2,737,165

GOVERNOR DEVICE Filed March 21, 1951 4 Sheets-Sheet 4 l I I" O P0511127 H Z /2P ATTOQNEK United States Patent 2,737,165 GOVERNOR DEVICE Robert H. Thorner, Detroit, Mich. ,ApplicationMarch 2i, 1951, Serial No. 216,821

" a7 clams. (Cl. 123-103 I This invention relates to internal combustion engines,

and'inore particularly toan improved internal combustion engine of the two-stroke cycle type, having means'gov'erning rvaria-ble performance factor 'or factors of said'e'ngine, such forinstan'ce as speed. The invention is particularly, butnotexclusively, advantageous in application to diesel engines of the foregoing type. 'The presentinvention is a continuation in part of my co-pending applications Serial No.':77,8'39 filed'February 23, 1949 for Governor/Mechanism and now abandoned; Serial No. 14,282, filed March 11,1948 for :Engine Governor, now Patent No. 2,66l;*728 issued December 8, 1953; and Serial No. 59,109 filed NovemberQ, 1948 for Engine Governor.

The necessity of controlling various performance factors v.of-diesel engines of the above type, particularlyY-the speed .thereof, .is an important requirement in practical use of such engines. However, provision insuch engines of reliable governing means and particularly of speed governing means presents a diflicult problem due to a nun iberof mutually exclusive and contradictory require-v mer ts which, if satisfied in a single device, make its .construction undesirably complicated and expensive, ;or its operation not fully reliable. With respect to ggoverning speed ,of diesel engines, it has beentound necessary to create -;a force which would vary as a function of-the-speed of ,the engine and then use thesame force to effect move. ats Q a ntrol me e s h s a f e pump rack, t s ver-. he s o e en neing theequired force is usually effected with the aid of ,so-called centrifugal gove ors including weights driven by the enginegan'd 4 2 rev n a n ula sp p p ional tothe speed. of th en n Wh le devi es Of hi u e-ha e n s d in co nectionwith-engines for a number otyears, there is a number of serious disadvantages in their-use, which disadvantages are well appreciated by those skilled in the .art. in first place, provision of a separate-rotating mechanism of a relatively complicated construction and means ot drivs ing thesame, complicates construction of the engi .1 ases s 1, and mak s maintenance re ica taud. costly. Insufii'cient sensitivity of governors manifesting itself in slow response, surging, hunting, and the resulting instability of the governed engines are further examples of such disadvantages particularly pronounced at lowerengin'espeeds,

Qne of .the' objects otthe present invention is to provide anfii'nproved governor for .an internal combustion in which disadvantages of conventional construct-ionsare overc n'ie and largelyeliminated and in which the desired speed controli's efiected in animprovedrnartner.

A fu'rther'object of the invention is to provide an p dve lsave nor r a n er m ustion ens-me is 2,737,165 Patented Mar. 6, 1956 "ice A still-further object of the present invention is to provide =animproved governor for an internal combustion engine of" the character specified in the preceding'paragraph, in which the final control member is actuated in response to 'and as a function of the speed of the engine.

A still further object of the present invention is to "provide an improved governor for an internal combustion engine having a charging blower, said governorhaving improved speed controlling means in which instability;

hesitation or hunting, low sensitivity and similar deficieir- 1 cies in performance are eliminated.

A' 'still further object of the present invention is'toprm vide an improved governor for an'internal combustion engine of the type specified above having'means whereby its'speed'is controlled in a dependable, consistent iatld stable manner throughout the entire .range of engine speeds,:including the low speeds thereof.

A stillfurther object .of'the present invention istoipriovide an improved governor for an :internal combustion I1gi11Q10f1he type specified, which governor includes'ra substantially frictionless servovalve or modulator valve, wherebyvirtually instantaneous response of the governor to changed condition, elimination of its hesitation and hunting, andstable operation of the engine are attained.

A-still further object of the present invention is to i'provide an improved governor for an internal combustion ng ne Qfth type pe u il ng the P es in th avengin a b x o th eng n as Vs/ asing factor or ultysniea s eing'pr vided to mp nsat 'tor he tfeet on .th -sant elled ens as p e f changes in air density resulting from hang s in ltitu and 9 tempera ure 'gt a r- 1;

It is an added object of the present invention to provide an imptovedgovernor-for an'engine of the foregoing. character, which is simple and rugged in construction, dependablerinoperation, andis relatively inexpensive to manufactureand ,to service.

Further objects and advantages of :the invention will beqapparent from the following description, takeningcon;

nection with the appended drawings, in which:

Fig. .1 is a sectional view illustrating (diagrammatically in part) a governor embodying the present invention, applied ,to a two-stroke cycle engine of the diesel type,

Fig.2 is an exploded view illustrating suspension means able etiect of the changes in air density produced by changes in temperature or elevation, or both.

Fig. .6 is a side view of the bi-metallic suspension spring torthe modulator valve of the construction of Fig.

Fig. 7 is a front ,view of the suspension spring of Fig. 6.. It is tobe understood that the invention is not limited in its application to the details of construction and.

arrangement of parts illustrated in the accompanying drawings,,since the invention is capable of other embodimer ts and of'being practiced or carried out in'ivar ious ways. Also it is to be understood that the phraseology or'lte minology employed herein is for the purpose 13f description and not of limitation.

i Inaccordance with the invention as applied'to a diesel engine of the two-stroke cycletype, I utilize as aspeetb sensing taculty Qr factor the pressure produced by the amp rn ta b owr, wh ch p s e v ies as a funetion 9f the spe ed of the engine. Since said pressure may 139i be sufiicient or dependable to actuate a control member directly by itself, I utilize, in my preferred form, as actuating or operating pressure for the control member the pressure of a separate fluid circuit having any desired intake and discharge pressures, and controlled by said sensing pressure. In order to effect the desired control, in the preferred form, I interpose in such fluid circuit a modulator valve adapted, when actuated through its predetermined range of travel, to modulate or to vary said actuating pressure throughout a range of intermediate pressures all the way from the intake pressure to the discharge pressure in said circuit. For proper operation the fluid circuit should have at least two restrictions with at least one of said restrictions being variable. I prefer, however, to use two restrictions with both being variable in a coordinated manner, such as by the use of two valves secured together for common movement. As one valve portion of such combined valve moves to close one restriction, the other valve portion moves to open the other restriction and thus to increase the effect of movement of the first valve portion on the static pressure in the circuit between the restrictions. It should be appreciated at this point that passages forming the circuit should have suflicient cross section and not be in themselves restrictive on the flow of fluid therethrough. I subjugate the modulating movements of such combined valves to the sensing pressure by actuating the modulator valve with the aid of a diaphragm or similar substantially frictionless means responsive to the sensing pressure. I use the operating pressure to actuate a pressure-responsive member, such as a piston, connected to the final control member, in the present embodiment the member controlling the speed of the engine, such for instance at the rack controlling the length of the stroke of the engine fuel pump.

By virtue of such a construction the speed-sensing pressure, which may vary through a very small range of pressures, is amplified in any desired degree or manner to produce operating pressure of any desired intensity and producing any required volume of transfer or flow of the operating fluid. This, in turn, enables me to produce controlling forces of any desired magnitude and acting through any desired distances, insuring proper operation of the engine control members.

According to the foregoing inventive concept in its broadest essential terms, a governor is provided which does not require a separate and costly driving element .designed and built in the engine and costly and complex engine-driven means in the governor itself. This undesirable requirement is avoided in the present invention by utilizing means inherent in the engine and rotating as a function of engine speed to blow air. The governor includes a pressure responsive member connected to be subject to a pressure which is a function of the pressure produced by the air-blowing means and varying as a function of the speed of the air blowing means. In the forms shown herein, the pressure responsive member (which actuates the modulating pilot valve) is subject to the pressure of the intake manifold and to the static pressure therein varying as a function of engine speed. It is within the scope of the inventive concept, which eliminates the need for separate engine-driven elements, that any air blowing means driven by the engine (and a part thereof) may be used to produce the pressures acting on the pressure responsive member and varying as a function of en gine speed.

While it is advantageous to utilize as speed-sensing pressure (brain" pressure) the charging air pump or other fluid pressure already available in an engine, under some conditions it may be desirable to provide a special source of such a pressure. For producing operating pressure any available fluid under pressure, dependent or independent of the engine speed, may be used to produce a fluid circuit. As a modified expedient, the sensing pressure itself may be used to produce such an operating circuit.

While various pressure-responsive means may be used foractuating the modulator valve, use of a diaphragm, bellows, or a disc is preferred due to sensitivity characteristics thereof in short stroke movements. For operating the engine controlling members, where relatively long movements are required, use of piston, long-stroke diaphragm, or like means is advantageous.

Improved means are provided for suspending the modulator valve to reduce greatly and virtually eliminate any frictional resistance to its operative movements, thereby insuring instantaneous response of the valve, facilitating assembling and disassembling of the valve mechanism, insuring its quick and easy positioning in proper functional alignment, and preventing disturbance of such alignment in operation. Use of such frictionless suspension means is of extreme importance, and it may be critical in most installations to which the present invention relates. Use of such suspension means is of a particularly critical importance in constructions wherein the sensing pressure is small. Such a leaf-spring-suspended pilot valve in operative combination with the substantially frictionless pressure-responsive valve-actuating member and the frictionless means biasing the pressureresponsive member provides a substantially frictionless sensing-mechanism which must respond to the small sensing pressure in the intake air passage produced by a small change in speed.

In order to compensate for the elfect of changes in air density produced by temperature variations, I use in one form a modulator valve suspension spring of bimetallic construction, to efiect in a desired manner the modulating positions of the valve. Similarly, sealed bellows are used to compensate for the effects of changes in air density produced by changes in altitude, and can also be made responsive to temperature effects.

While the invention is illustrated and described with reference to a two cycle diesel engine, it will be understood that it is not limited thereto, and may be used with an equal success with any engine having a source of air pressure varying as a function of the speed of the engine.

In the drawings there are shown by way of example diesel engines of the two-stroke cycle type, embodying the present invention. Referring particularly to Figs. 1-3, the diesel engine illustrated therein comprises a cylinder 1.0 in which there is slidably fitted a piston 11 having 2. connecting rod 12 operatively associated with the crankshaft 13. Fuel injection means 14 and exhaust valve are provided at the top of the cylinder 10 in a manner well known in the art. An air pump or blower 15 driven by the engine is provided, as shown. The blower 15 delivers air into an air box 16 surrounding the cylinder 10. A plurality of ports 17 lead from the air box 16 into the lower portion of the cylinder 10.

A fuel injection pump 25 which may be of any suitable construction has a fuel metering rack 26 provided therein. The rack 26 constitutes the speed controlling member of the engine. Moving the rack 26 to the right reduces the amount of the fuel discharged through the fuel injector 14, reducing the speed of the engine. Moving the rack 26 to the left increases the amount of fuel discharged through the injector 14, thus increasing the speed of the engine.

The structure so far described is conventional; its construction and operation are well known in the art and therefore need not be described in further detail. It will suffice to mention that the first portion of the downward stroke of the piston is a working portion of the stroke. As the piston reaches the second portion of its downward travel, the exhaust valve opens, permitting a part of the exhaust gases to escape. Near the end of the downward stroke of the piston the air ports 17 are uncovered, and

fuel is injected intothe cylinder, -and: ignition takes plaee, stanting the-pistonlon its downward'traiiel.

ltihave founduthat theair pressure v in lthei-boxl6 waries as-a function ofthe speed oftthe engine. Thus, in=.accord-. anee with the invention, the; air pressure :in theihox116 qualifies as a speed sensing faculty orafactorifor controlling the engine. However, in-accordance with the inven-. tion, said pressure may not qualify as suitable power pressurc'foridirectly actuating thetspeed controlling meme berof' thev-engine, Lthe=met6ring rack 26 in the'present embodiment. Such pressure is 1 particularly unsuitable r-Ihelcwerespeeds of the-rengine,zwhere its changes are inedeqlletetto insure proper control of the engine. It :is at :such-speeds that the box air pressure particularly requires amp ification.

acorn-dance; with Iheinveution. a fluid circuit is provided t produce the requircd operating" pressure :for u. ugnh piston connected to the metering rack-.26. j i'hG 1Ql1SHUfiQ 1 :of Fig. 1,: such a circuitcomprises .ia l m 'n .fluidaprcssurein theform ofthe eng n Oil Pll p 30;yyith aconventional pressure relief valve (not shown), a Qischarge conduit 31, a chamber 32, :a valve chamber 33, a1charnber 34, and-acondnitSS leadingto-the engine crankcase and the intake conduit 29 ;of .the oil pump 30. l ai e hamber 33 i lfq mcd by ,a' recess orlbore provided in the body 36 and end pieces 37 and 38 closing the-ends of the bore. The end piece 37 .is connected ;to e b 1 2 n a y su ab e mann r, such as with the raid of. screws 39, while the end piece 33 .is-pressed into the bore. End pieces 37 and 38 have valve orificesorsopens 0am res c ve y p cv ed th rein.

11 t e c am r the e. is su pe dedinazmanner lcd in det l l w combin d mod atgror pilot valveAZ haying valve portions or faces 4; and 544:,pro-

its ends and adapted to cooperate with openings 4.0 end u, respectively, to vary their effective areas through therange of areas frornzero to their full Vefiecr tive areas. The stern .4-5 of the valve 42 extends through the I ening ll and is supported at thehole 4,6 provided inthe leaf spring 50 secured to the body 36 with ihcaid of a, screw 52. 'Ashoulder 5 3 is provided on :thestem 45. to bear against the leaf spring 59. "A stern-47 haying shoulde pas s i us th l 3 q athie leaf spring 51 ,s e cured to the bodyfip withthe aid'pf-a screw 49. n

.Thesterns 45 and 47 are arranged co-a xially with the P. ,l es .4!) and 1 in o d to ins pr ne andefu seating of the valves forclosing the openings. Means are provided to insure such arrangementof the valves in assembly. Such means are exemplified by the elongated o .55 pr i the upp raend of thelc f-snrinss 5Q and 5 1; and anti-torque plates 57-ancl 58 at serevvs 42 and 52, respectively. It will be clear from an egt; arnination of the drawings, that theprovision ofthegelon;

gatedhglc S SenabIesquick and easy locating ofthe valve qdy n'axia ly l th op n n b rs s sthe a cin the'jend piece and thereupon tightening of the respective screw. The elongated hole vor similar fastening clearance means, permits the valve faces 43 and 44 to seek any desired position in relation to their seats and 41, respectively; after which the screws .49 and .52, respectively, are tightened. The anti-torque plates uhich'fit into the body recesses and cannot rotatevtherein prevent direct contact' between the screws and the leaf springs and the tendency .of the screws in tightening .to tnrn the springs and'lhus to disorganize the'previously attained concentricity of valve positioning. The anti torque plates arernadeof spring steel and are provided with a bead in order fto produce a lock washer action at the screw-in I addition to its antietorque action. Use of-alock washer and a fiat plate niayalso be advantageous;

The end of the valve stem 47 protruding from the leaf spring '51 fits into a bore' lprovided in .the end of adia- Pb. ene 59 d sh nl ersdthe eq f any s itabl m ans e used to ecureat least The diameterofsaid retainer .end is apprcximatel-nequal to thatof the shoulder 54, and theleafspriug 51.1s held between the shoulder: 5.4.. a'ndithe diaphragm-retainer and "is also .soldered thereto, thus preventingvrotation 0151119 valve and making ,itsseating moredefinite. ,An assemblyis produced comprising the valve 142 positively secured to the leaf spring 51, with end-piece 37 fittinglooselybetween leaf spring 51 and valve face 43. "This assembly .is installed in the governor by first inserting-the valve flange 53 and stem 45 through orifice 41 in end-.pieceiSS. Then the screws 39 are tightened to secure end-piece to the ;body 36. ,The leaf spring with itsanti-torque plate 53 is thenloosely secured to the body 36 byscrlcw 52 after first-slippingthe hole .46 of leaf spr-ing'50 .over

the extension of stem 45.0:1- the end ofsthe-valve 42; the

hole 46 is made for a slipfit clearance withi-the extension of stem 45. The leaf; spring 50 may be slightly .preib ent; in its free positionto the left, .asiyiewed in'Figl; tolpro- :vide an abutting contact :of the leafuspring-againstshoul- I der 53 when screw 52 is tightened which straightens'out the spring 50 as shown, but with a very slight leftward force on shoulder v53 This slight'pre-bending of the spring 5%) aids in maintaining the valve 42 in position whereby the leaf spring 59 will always followmovements i of the valve, and further facilitates easyassembly of the unit by avoiding the additional complexity Of1pOSitiVei$ curing means at this leaf spring suspension; however suitable positive securing means may be employedifdesired. Next, the leaf spring 51 and its antietorque plate 57 are loosely secured in position by means of .screvv .49;

Then theqvalve 42 is held manually to theright asviewefd in Fig. 1, so face 44 seek-sits seat in orifice 41 whereupon i the screw 52 is tightened; similarly, the-valve is next held .rnanually t he:lcf f ce 43 seeks its seatin orifice 1.411 whereupon-screw .49 is tightened. For best results, .the

procedureis repeated .a second time at each-seat byfholde ing the valve face tightlyagainst its respective seat .and then slightly loosening'the corresponding screw andltighh eningagain. 'lfhe recess inzthe body 36, as-shownibest in Fig, 2, proyides arotary abutment for the anti-torque plate 57 as it tends to revolve due to the tightening action of the head ofscrew '49 wherebyonly thrust forces are transmitted to leaf spring 51-so th,at its .position is not disturbed by tightening screw 49. As illustrated in this disclosure,;.the side walls .ofqthe recess forzthe anti-torqueplate provides the rotary abutment, although if desired,

the top wall of the recess may be employedequally'cwell' By virtue of such a construction thehole or similar means to permit :universal. movement of 1 9 Ankle, the anti torque plate, :and positive lockingl o'f the valve from rotary movement is capable of providing"? me'u ai in Su stan ial y e -p f a s; :and' 'if greater mpontance, substan iallyfrictionless valve seat-- ing in all production units. Mis-alignment of thevalve vfaces in relation to their seats in :the end-pieces, as ex-T plained, could be produced by the torque of SGIEWS'fQ a .2, or t leaf spring holes and :the threaded bores; for-f screws .49 and 5-2 or if the valve can revolve in relation to" the springs iii and 51 wherein mis-align i ment could be; produeed, .fcr example, as .a result-of a slight-bend in the valve due to.machiningzstresses;whichi bend would produce eccentric movement upon rotation of the valve. Such nus-alignment of.a valve face in relation to-its seat would cause a wed-ging actioh wherein considerable static friction is produced to' prev'eiit' valve from instantly leaving its seatwhenireguii'ed the stabilizing process. 'Thiswedging action would since only one sideof the valve would contact the and the tapered form of the valve would further ;in producing :the :we'dg'ing action when t he-valve is it either extremity of travel. Such wedging action disrupts the inherent frictionless characteristics of the combination of the diaphragm or similar frictionless sensing memher, the leaf-spring-suspended pilot valve, and the frictionless biasing spring 76, which combination must respond consistently to the minute changes of the variable factor which initiates operation of the device. In the embodiments illustrated herein, the variable factor is engine speed which is manifested in the form of relatively low pressures varying as a function of engine speed produced in chamber 72 by blower 15. But these features ofmy invention are equally valuable in any control mechanism wherein frictionless characteristics are desired in responding to any other variable factor such as torque, pressure, velocity, etc. Actual experience with a governor having this valve construction and misalignment of the valve and its seats produced surging and hunting, whereas very stable operation was easily achieved with the anti-torque plate, the elongated hole 55, and the valve secured from rotation by suitable means. These features are particularly valuable in order to build the governors in production.

A conduit 60 provides a communication between the valve chamber 33 and the right hand side of the cylinder 61, wherein there is slidably fitted a piston 62 having a piston rod 63 connected to the metering rack 26. The left-hand side of the cylinder 61 communicates through a conduit 64 with the chamber 34 and houses a compression spring 65 urging the piston 62 to the right. Thus the piston 62 is subjected to forces produced at one side thereof by the pressure existing in the valve chamber 33, andon the opposite side thereof by the forces produced by the pressure existing in the chamber 34 and by the spring 65. As the'pressur'e in the chamber 33 increases, the piston 62 is moved to the left in opposition to the spring 65, whereby the metering rack 26 is moved to increase the fuel discharged by the fuel injector and thus to increase the speed of the engine. Decrease of the pressure in the valve chamber 33 has the opposite effect.

It will now be understood in view of the foregoing that pressure in the chamber 33 is controlled by the movements of the modulator valve 42, and that it varies in magnitude from a pressure equal to that at the discharge side of the circuit (when the valve 42 is in the position designated by the numeral 66 and closes the opening 41) to that at the intake side of the circuit (when the valve 42 is in the position designated by the numeral 67 andcloses the valve opening 40). Intermediate positions of .the valve 42 produce an infinite number of intermediate or modulated pressures.

It should be also appreciated that the valve portions 43 and 44 aid each other, and as one of them opens a restriction the other operates to close the other restriction thus adding to the effect of opening the first restriction.

In accordance with the invention the desired type of movements of the modulator valve 42 is produced by actuating it with the aid of a relatively large diaphragm 70 made of. suitable material, such as synthetic rubber, and having desired characteristics, particularly high sensitivity. By virtue of such actuation there are effected steady but instantaneous responsive movements of the modulator valve free of frictional resistance since the diameter of the diaphragm is large in relation to its short travel. By exposing the diaphragm 70 to the action of the speed-sensing pressure in the air box 16, movements of the modulatorvalve, as well as the resulting pressures in the valve chamber 33 and movements of the piston 62 and of the metering rack 26 are subjugated in a desirably reliable manner to said sensing pressure and consequently to the speed of the engine.

In the present embodiment of the invention the diaphragm 70 is held at its peripheral edges between the body 36 and a cover casting .71 forming a chamber 72 communicating through a conduit 73, with the air box 16 and thus exposing the left-hand side or surface. of the diaphragm to the action of the speed-sensing pressure. At its center, the diaphragm 70 is held between the shoulder of the diaphragm retainer 59 and a nut 74 screwed on the extension of the retainer 59. The diaphragm may be secured to the valve either before or after assembling the valve structure as previously described. If the diaphragm is secured to the valve after installation of the valve assembly, the diaphragm is first inserted in place and the nut 74 is installed and tightened by holding the fiat extension of the retainer 59 to prevent rotation thereof and hence undue stresses on leaf spring spring 76 acts on the modulator valve 42 without friction in opposition to the forces produced by the pressure acting on the diaphragm 70, to balance said forces and to establish the required balance at the desired speed of the engine.

Means are provided to adjust the point of such balance and thus to vary selectively the governed speed of the engine. In the present embodiment said means are exemplified by the linkage 80, 81, and 82, fulcrumed as at 83 and operatively connected to an adjusting screw 84. Rotating the screw 84 varies the tension of the spring 76 and thus regulates the governed speed of the engine.

Thus the combination of the substantially frictionless diaphragm 70, the leaf-spring supported modulator valve 42, which is often called a pilot-valve in most servomechanisms, and frictionless biasing spring 76 form the sensing mechanism previously referred to, which must respond without delay to the minute sensing pressures produced by small changes in the blower pressure in box 16 accompanying small changes in engine speed. It has thus been shown that the movements of the sensing mechanism in my governor combination in responding to these minute sensing pressures are substantially frictionless.

By virtue of such a construction increase of the speed of the engine, and consequently of pressure in the air box 16 and chamber 72, causes the diaphragm 70 and the valve 42 to move to the right (see Figs. 1 and 3), decreasing the effective area of the valve opening 41 and simultaneously increasing the effective area of the opening 40. Such a condition immediately causes decrease of the pressure in the chamber 33 and the right hand side of v the cylinder 61, allowing the spring 65 to move the piston 62 to the right and to actuate the metering rack 26 to decrease the amount of fuel discharged by the fuel injector into the cylinder of the engine. This, in turn,

causes decrease in the engine speed and the air pressure in the box 16 to a value at which the system comes to a balanced condition at a certain engine speed. It should be appreciated that pressure in the chamber 34 being, in effect, atmospheric pressure, remains constant. Decrease in the engine speed brings about a reverse operation of the governor.

The construction illustrated in Fig. 4 is similar to that The flow of air from the chamber 91 to the I chamber through the control chamber 95 is controlled :9 by the modulator -.valv.e :96. In .this construction ,it :is particularlyjimp'ortant that :theconduit 193 is ofarsufli: cient-cross section and does not have restrictive effect. In its other particulars .of construction and operation the system of Fig. 4 is similar to .the system of Figs. 1-3.

lt should be appreciated that as the density of the atmospheric air changes, the point of balance of the operative parts of the governor also varies, thus aifecting the governed speed of-the engine.- While the effect of the resultingvariations in engine speed is rather small and may be safely disregarded in many applications, my improved governor may, if desired, be provided with means compensatingfor changes in air density resulting from changes in temperature, altitude, or both. By virtue of such a construction extremely close regulation, unafiected by changes in air density is effected.

Whe'n changes in density, and hence the sensing pressure,-are expected to be caused primarily by changes in t he arnbient temperature, one or both of the suspension springs-101 may be made of bi-metal construction, as illustratedin Figs. 5 and 6. As the ambient'temperature increases and the resulting decrease in the air density causes'the governor to operate to efiect increase in engine speed, the bi-metallic spring tends to bend as illustrated in Fig. 6 in dotted lines. Such tendency causes application of a certain force on the modulator valve toward the left, which condition tends to cause a corresponding' decrease in the engine speed, thus compensating for'the undesirable eifect of the change in air density. Decrease in the ambient temperature causes the bi-metallic spring to affect operation of the governor inareversed manner.

The above-described means may be used with success in'ground installation where .variationsin engine speed caused by the effect of changes in barometric pressure are immaterial. In aircraft and similar installations, where considerable changes-in altitude are expected, means illustrated in Fig. 5 may be employed. The diaphragm and-valve in Fig. -5 are in a reversed position from .that shown in Figs. 1 and 4.

'The means illustrated in Fig. 5 take advantage of the. fact that a-completely evacuated and sealed capsule or bellows is responsive substantially to only the pressure of the-surrounding medium, such as the atmosphere. If, however, such a sealed capsule or bellows is partially filled-with'a gas, such as air or nitrogen, it becomes responsiveto the temperature as well as the pressure of the surroundingmedium; andthe denser the gas inside thebellows or capsule, the more responsive is such a unit to' the ambient temperature.

In-accordance with the invention, -I provide in my device a suitable bellows completely evacuated or partially lilledwith-suitable gas and adapted to act on'the modulator valve to affect its operation in such a manner as to compensate for changes in air density produced by changes'in altitude or in altitude and temperature, respectively.

One such construction is shown in Fig. 5, wherein a compression spring 105 bears on the left hand end of themodulator valve 106 to oppose the sensing forces produced by the blower and exerted on the valve by the diaphragm 107. A spring retainer 108 slip fits over the end of the stem of the modulator valve 106 to guide one end of the compression spring 105, the piston109 being'manually actuated as in the construction. of Figs. 1-4 writer the same purposes. A bellows 110, which maybe either completely evacuated or filled with gas as explained above, is operatively arranged in a chamber pene 1 t e atmosp e n formed y a h u ina l securedto the body 112 of the governor. The bellows 110 has oneend soldered to the end piece 113 press fit into the end of the housing 111, while a shaft' abuts at-its other end. Aspring 115which has rate lower a tha -10 the mai Spring is ns a dbetween the diaphragm "107 and the shaft 114. A spring retainer 116 saidfir'S't-narhed direction and for fr icti'onless'suspensi is -secured .-to:.the diaphragm 107-in=any suitable manner 5 .changes in altitudeor in altitude and .pressure.'(depending on whether-it is fully evacuated or gas-filled), a slight force. is exerted'on the modulator valve affecting its operation in a .predeterminedmanner to compensate for the undesirable effects of such changes. By-installing the bellows .toYact directly on the main spring 105, its

compensating effect can be made more pronounced.

Itshouldalsobe appreciated that the bi-inetallic suspension spring operates'similarly to the gas within the bellows to compensate for temperature changes, and these-two expedients maybe used either independentlyforthe same purposes, or in" a combination to aid'each other. By virtue of the above constructions the objects ofsthe invention listed above, and numerous additional advantags are attained. i 0 -I claim:

1.1-In a governor'for an engine having means toproduce a chargiug'pressure that' varies 'as a fuiictionof the speed of thecugihe and a control means fto' regulate the speed of the engine, the combination of means to effect movement-ofsaid controlmeans "comprising, a pressureresponsive member connected to said control means for actuation thereof, a pressure fluid circuit communicating with said" pressur responsive member, valve means" said circuit tddireet -pressure fluid to said pressure responsive member to effect a speed controlling movement ofsaid control member, substantially frictionlessswing able means haying:awidthimparting rigidity y, rectio'n' acting to sup ort said valve ea s forsu tiaIly frictionless movements in a direction transvers to within'fthe fluid controlled thereby with only lfluid co'n ct at the flow bm ningsurraees thereof during operational movements, at substantially frictionless second press" responsivemembenconnected to said valve means f r actuation thereof, 'a passage connecting said second pi;

sure responsive to said pressure tl'ia't v ari esias a u 9n qt engi e spe d. a d b fimt a l i tifin 5 a in u ens'f n qs f r Rl'oduced by sai secon pressure responsive membe'r'as a resultof said last named p ssu ac g th apy r y t c ln i ed Q mntsof said valverneans, said second pressure resp on-. sive member and said biasing. means are substantially fric tionle's sand" thereb respond to minute changes in Sgt d pr sure hat v s a al ji i t qa 9t .eus n pg d al eci asin ZQ TKI? -QQI ll netiQ o m an? fi diu c a m which, said swin able means comprises a pair of spa or n en ne hav n means, to p o". ,e th t va e a im' t f ,7 e a d a c t m n to egul e e. @993 the c im h m i m o mean to 0 effect movement of's a id control means comprising,

p asu emsspon' memb con ect d t a cont e means foraptuat on thereof, a pressure. fluid circuit stantially frictionless second pressure responsive member connected to said valve means for actuation thereof, a passage connecting said second pressure responsive member to said pressure that varies as a function of engine speed, and substantially frictionless biasing means opposing forces produced by said second pressure responsive member as a result of said last named pressure acting thereon, whereby the combined movements of said valvemeans, said second pressure responsive member and said biasing means are substantially frictionless and thereby respond to minute changes in said pressure that varies as a function of engine speed to effect movement of said first pressure responsive member and cooperating control means to maintain the speed of the engine.

4. In a governor for an engine having an intake passage and a charging blower therein driven by the engine that produces a charging air pressure in said passage that varies as a function of the speed of the engine, and a fuel control means to regulate the speed of the engine, the combination of means to effect movement of said fuel control means comprising, a pressure responsive member connected to said control means for actuation thereof, a pressure fluid circuit communicating with said pressure responsive member, valve means in said circuit to direct pressure fluid to said pressure responsive member to effect a speed controlling movement of said control member, substantially frictionless swingable means having a width imparting rigidity in one direction acting to support said valve means for substantially frictionless movements in a direction transverse to said first-named direction and for frictionless suspension within the fluid controlled thereby with only fluid contact at the flow controlling surfaces thereof during operational movements, at substantially frictionless second pressure responsive member connected to said valve means for actuation thereof. a passage connecting said second pressure responsive member to said charging air pressure, and substantially frictionless biasing means opposing forces produced by said second pressure responsive member as a result of said last named pressure acting thereon, whereby the combined movements of said valve means, said second pressure responsive member and said biasing means are substantially frictionless and thereby respond to minute changes in said charging air pressure to eifect movement of said first pressure responsive member and cooperating control means to maintain the speed of the engine.

5. Ina speed governor for an engine having an intake passage for the flow of air therethrough, said engine including means to produce air pressure in said passage that varies as a function of the speed of the engine and a control means to regulate the speed of the engine, the combination of means to effect movement of said control means comprising, a pressure responsive member connected to said control means for actuation thereof, an air pressure circuit communicating with said passage air pressure and with said pressure responsive member, valve means in said circuit to direct air to said pressure responsive member to effect a speed-controlling movement of said control means, substantially frictionless swingable means disposed to impart rigidity in one direction acting to support said valve means for substantially frictionless movements in a direction transverse to said first-named direction and for frictionless suspension within the air controlled thereby with only air contact at the flow controlling surfaces thereof during operational movements, a substantially frictionless second pressure responsive member connected to said valve means for actuation thereof, said second pressure responsive member communicating with said passage for movements in response to-changes in engine speed, and substantially frictionless biasing means opposing forces produced by said second pressure responsive member as a result of said passage air pressure'acting thereon, whereby the combined movements of 'said valve means, said second pressure responsive member, and said biasing means are substantially frictionless and thereby respond to minute changes in said passage air pressure to effect movement of said first pressure responsive member and cooperating controlmeans to maintain the speed of the engine.

6. A control device to operate a movable controlled member in response to changes in a variable factor and having a stationary part comprising, a pressure responsive member for actuating said movable controlled member, a pressure fluid circuit communicating with said pressure responsive member, valve means in said circuit to direct pressure fluid to said pressure responsive member, said valve means including a seating member and a valve body member, a substantially frictionless swingable member having a width imparting rigidity in one direc tion acting to support one of said valve members for submeans responsive to said variable factor to exert forces on said valve means as a function of said variable factor, and substantially frictionless biasing means to oppose said forces, whereby the combined movements of said valve means, said sensing means, and said biasing means are substantially frictionless and thereby respond to minute changes in said variable factor to effect movement of said controlled member.

7. A control device to operate a movable controlled member in response to changes in a variable factor and having a stationary part comprising, a pressure responsive member for actuating said movable controlled member, a pressure fluid circuit communicating with said pressure responsive member, valve means in said circuit to direct pressure fluid to said pressure responsive member, said valve means including a seating member and a valve body member, a substantially frictionless swingable member disposed to impart rigidity in one direction acting to support one of said valve members for substantially fric tionless movements in a direction transverse to said firstnamed direction and for frictionless suspension within the fluid controlled thereby with only fluid contact at v the flow controlling surfaces thereof during operational movements, threaded fastening means including a head means to secure said swingable member to said stationary part of said device, an anti-torque member between said head and said swingable member and cooperating with said stationary part to prevent the torque of said head from acting on said swingable member when said fastening means is tightened, whereby only thrust forces are applied to said swingable member to maintain alignment of said supported valve member in relation to the other of said valve members, substantially frictionless movable sensing means to exert forces on said valve means as a function of said variable factor, and substantially frictionless biasing means to oppose said forces, whereby the combined movements of said valve means, said sensing means, and said biasing means are substantially frictionless and thereby respond to minute changes in said variable factor to effect movement of said controlled member.

8. A control device to operate a movable controlled member in response to changes in a variable factor and having a stationary part comprising, a pressure responsive member for actuating said movable controlled memher, a pressure fluid circuit communicating withtsaid pressure responsive member, valve means in said circuit mamas 13 to direct pressure fluid to said pressure responsivemember,i.saidvalve means including a se'a'ting' memberrandta valve .body member, a substantially frictionlessfswingable member disposed to impart rigidity .in. one directionact ing-to support one of said valve members: for substantially' frictionless movements in a directiontransverse to said first-named direction and for frictionless suspension with in the fluid controlled thereby with only fiuidmontact at theflow controlling surfacesthereof during operational movements, threaded fastening means including a head means to secure said swingable'memberto saidstationary part of said device, said swingable member having sufficient clearance relative to said fastening means for self-aligning seating of said supported valvelmember in relation to the other of said valve members when said fastening means is tightened, an anti-torque member between s'aid head and swingable member and cooperating with'said stationary part to prevent the torque ofi-said head from acting on saidswingable member -when said head is tightened, whereby only thrust-forces a're applied to said swingable member to 'maintainalignment ofs'aid supportedvalve member in relation to member of'sai'd valve members, substantially frictionless movable sensing means to exert forces on said val-ve mean's' as 'a function of said variable factor, andsubstantiallyrid tioril ss biasing'means to oppose said forces, whereby the combined movements of said valve means, said sensing means, and said biasing meansare substantially friction les's'jand thereby respondto minute changes in said-Vail direct pressure fluid to said pressure responsive 'rnerribe'f,

said valve means including a seating member and a valve bodymember, a substantially frictionless'swing'able meniber'disposed to impart rigidity in one direc "nae 'ng'to support one of said valve members for subst tieillyf ctionle'ss movements in a direction transverse to 'aid fi rs'tnamed' direction and for frictidnl'ess"suspensidifwitliin the'fluid controlled thereby with only fluid '6 tact atthe flow controlling surfaces thereof during' 'ope ments, said supported valve memberibeingpo p to said swingable member to prevent r'otafy-r'riovement of said supported valve member "wheres/en amerit of said two valve members are maintainedl sub st tially frictionless movable sensing means to" ester: fdrceso'n said valve means as a function of said variable factor, and substantially frictionless biasing means'to' e 5 pose said forces, whereby combined'movemnts"of said va e means, said sensing meansfand "s'ai'dbi' "mg 'fneans are substantially frictionless anw'th'resy tension To te changes in said variable fac'tonto effect in enient of said controlled member. m

A control device to operate a movable controlled m berl in response to changes in a vafiablfe factor and having a stationary part comprising, a pressure responsive f er for actuating said movable controlled merriberj 'a pressure fluid circuit communicating with said pressure re sponsivemember, valve means in said" circuit to 'dir'eet pr" ure fluid to said pressure responsiveim mber','jsaid va e means including a seating member and avalvebody member, a substantially frictionless swifi 'gabldmember di sed to impart rigidity in one direction ac ing-resuspi; tvonerof said valve members for substantially fficti o less movements in a direction tfansverselto said firstnamed direction and for frictionlesssuspension withinthe fluid controlled thereby with only fluid contact at tiiie'fldw contro lling surfaces thereof during operational movesaid sfasteningr means for selfr-aligning." seating of said-supported-valvetmember in relation'to the other of said-valvemembers' when said -:fas.tening means istightened, said supported valve: memberibeing positively "secured to said swingable member to preventrotary movement v.ofsaid supported-valveamember-whereby alignment ofsaid two valve members'are maintained, substantiallyfrictionless movable sensing means to exert-forces onsaid vfalvemea'ns as a-functionio'f said variablefactor, andsubstantially frictionless biasing means to. opposesaid forces, whereby combinednio-vements of s'aid' -valve means, saidsensing means, a and said biasingmeans are substantially frictionless and thereby respondto minute changes in said .variable factorto effect I movement of said controlled 1 memr be'r.

'11. A control device to operate a movable controlled member in response to changes ina variable factor and having 'a "stationary part" comprising, apressure responsive 'memberfor actuating said-movable controlled member, a pressure fluid circuit communicating with said pressurerespon'sive member, valve means-in said circuittto dir'ect pressure fluid to 'said pres'sure responsive vmember, said valve m'eans including-a seating member and a valve body member; a substantially frictionless swingable 'meinbef having -a width imparting rigidi ty in one directiori acting: to's upportone ofsaid valve members for substantially frictionless movements in adirection transverse to"said"fir'st nar'ried direction'and for frictionless suspension within the fluid controlled thereby with only fluid confa'ct' at the gnaw "controllingsurfaces thereof during operni sarrnevemems; threadd fastening :means in= means to-se'curesa-id swingable member part-ofisaiddevice, said'swingable menibef "liavingsuiii'cieiit clearance relative to said fastening meanls for self aligning i seating of said supported" valve In "befinrelation to th'e' ther of saidvalve members when said fasteriing' rnans'istightened, an anti-torquemember' between said'h'ead andisai'd -swingable member and cooperating with 's'aidistationarypart to prevent the torque' Eif said'liead-froni a ing onsaid s'wing'ablefrnembe'if when said fastening ineansis tightened,wherebyonly. thrusf'f'or'ces are applied t'd' said swingable memberito maintain'a'lignment of' s'aid supported valve member in relation" to the other" of" said valve members, said supsported "valve" member being positively secured to said swingable" ember-to prevent-rotary movement .of said supported "v lve member -'-whereby'-alignment of said two valve m m s are maintained; substantially frictionless msvabiesensing' mean d'er'ert forceson .said valve ,n-manfs'as a'ff" 'ctioii said-variable'factor, and substannatty" frictionless whereby: the combined movements of "said valve means, said sensing means;andsaid"biasing'means are substantiallyfric ro'rll'ess' and thereby 'resp'o'nd'to" minute. changes ,x.in saidvariable'faetofto effect' movement of said cdnments,' fastening means to secure"saidswingablefiiem-' trolled member;

1 2. In a fluid mechanism having a stationary part and a pressurefluid irctiit therein," two orifice seating members iii series in said'circuit, 'ava1vemeinbefihavii1g 1W0 valve-mess to'modulate simultaneously the aperture ofeach of said orifice seating members, respectively, for. controllingfluid pressure in said circuitbetween said two orifice'se'ating members, one of said 'valve faces increasing the aperture of itssaid cooperating-orifice seating membe'r, *while'lhefothei- "of 'said valve'faces decreases theapnure of its said cooperating orifice seating-merriher, two spacedsiibstantially frictionless swingable member'sdisposed to' impart rigidity in one direction acting to's pport said' valveinember for substantially frictiongessfmevement in a directiontransverse to said firstnameddirectidn and fo'r'frictionle'ss suspension within the fluidcontrolled'thereby withonly'fluid contact at the fiowfcontrolling surfaces thereofduring operativemovem'ents', separate fastening means-to -secu'r'e each of said ,swing'able members, respectively; between said stationary asing' ineansto 'oppos'e' said forces,

part and said respective fastening means, each of said swingable members having means to produce clearance relative to its respective fastening means for self aligning seating of each of said valve faces in relation to their respective seating members.

13. In a governor for automatically controlling the speed of an engine having an intake passage and a charging blower therein that produces a charging air pressure that varies as a function of the speed of the engine, and control means to regulate the speed of the engine, the combination of means to eflfect movement of said control means comprising, a pressure responsive member connected to said control means for actuation thereof, a pressure fluid circuit communicating with said pressure responsive member, valve means in said circuit to direct pressure fluid to. said pressure responsive member to effect a speed-controlling movement of said control member, a second pressure responsive member connected to said valve means for actuation thereof, a passage connecting said second pressure responsive member to said charging air pressure, and biasing means opposing the forces produced by said second pressure responsive memher as a result of said last named pressure acting thereon.

14. In a self-regulating control mechanism for automatically controlling a variable condition the combination of, control means to regulate said controlled condition, a pressure responsive member connected to said control means for actuation thereof, a fluid circuit having a flow of fluid therethrough and communicating with said pressure responsive member, valve means in said fluid circuit for directing fluid therein to said pressure responsive member for effecting movements thereof, said valve means including a valve body member and a mating member cooperable therewith, a leaf spring member having width imparting rigidity in one direction acting to support one of said valve members for substantially frictionless movements in a direction transverse to said firstnamed direction and to prevent surface contact of said supported valve member during operational movements thereof, said leaf spring member having only one fixed support in substantially its own plane, substantially frictionless movable sensing means responsive to changes in said controlled condition and acting on said supported valve member to effect movements thereof for producing movements of said pressure responsive member and thereby amplified forces acting on said control means, substantially frictionless biasing means opposing the forces produced by said sensing means, whereby the combined movementsof said supported valve member, said movable sensing means, and said biasing means are substantially frictionless and thereby respond substantially instantaneously and consistently to minute changes in the forces produced by changes in said controlled condition acting on said sensing means to effect movement of said control means for maintaining within a predetermined variation a desired value of said controlled condition.

15. The combination of elements defined in claim 14, and said fluid circuit including at least two restrictions, said pressure responsive member communicating with said circuit at a point between said two restrictions, said supported valve member varying the restrictive effect of at least one of said restrictions to modulate the pressures acting on said pressure responsive member.

16. The combination of elements defined in claim 14, and a second leaf spring member similar and substantially parallel to said first leaf spring member to assist in supporting said supported valve member, said second leaf spring member also having only one fixed support in substantially its own plane, variable force second biasing means acting on said pressure responsive member to oppose the forces produced thereon by fluid pressures in said fluid circuit acting on said pressure responsive member, the force of said last-named biasing means varying as a function of the movement of said pressure respon- 16 sive member, said valve means controlling pressures on only one side of said pressure responsive member, the configuration of said valve body member in relation to the said mating member adapted to produce modulated pressures acting on said pressure responsive member to effect movement thereof as a function of the movement of said supported valve member, and the force of said frictionless biasing means varying as a function of the movement of said supported valve member, whereby the movement of said valve means varies as a function of said controlled condition to effect corresponding move ment of said control means also as a function of said controlled condition.

17. In a governor for automatically controlling the speed of an engine comprising in combination, control means to regulate the speed of the engine, a pressure responsive member connected to said control means for actuation thereof, a fluid circuit having a flow of fluid therethrough and communicating with said pressure responsive member, valve means in said fluid circuit for directing fluid therein to said pressure responsive member to effect movement thereof, said valve means including a valve body member and a mating member cooperable therewith, substantially frictionless swingable means disposed to impart rigidity in one direction acting to support one of said valve members for substantially frictionless movements in a direction transverse to said firstnamed direction and to prevent surface contact of said supported valve member during said operational movements thereof, substantially frictionless movable sensing means responsive to changes in engine speed and acting on said supported valve member to effect movements thereof for producing movements of said pressure responsive member and thereby amplified forces acting on said control means, substantially frictionless biasing means opposing the forces produced by said sensing means, whereby the combined movements of said supported valve member, said movable sensing means, and said biasing means are substantially frictionless and thereby respond substantially instantaneously and consistently to minute changes in the forces produced by changes in engine speed acting on said sensing means to effect speed-controlling movements of said control means for maintaining within a predetermined variation at desired value of engine speed.

18. The combination of elements defined in claim 17, and said fluid circuit including at least two restrictions, said pressure responsive member communicating with said circuit at a point between said two restrictions, said supported valve member varying the restrictive effect of at least one of said restrictions to modulate the pressures acting on said pressure responsive member.

19. The combination of elements defined in claim 17, variable force second biasing means acting on said pressure responsive member to oppose the forces produced thereon by fluid pressures in said fluid circuit acting on said pressure responsive member, the force of said lastnamed biasing means varying as a function of the movement of said pressure responsive member, said valve means controlling pressures on only one side of said pressure responsive member, the configuration of said valve body member in relation to the said mating member adapted to produce modulated pressures acting on said pressure responsive member to effect movement thereof as a function of the movement of said supported valve member, and the force of said frictionless biasing means varying as a function of the movement of said supported valve member, whereby the movement of said supported valve member varies as a function of engine speed to effect corresponding movement of said control means also 'as a function of engine speed.

tions in said circuit, said communication of said pressure responsive member with said circuit being at a point beber, the force of said last-named biasing means varying as a function themovement of said pressure responsive member, said supportedvalve member being disposed to vary the restrictive eifect of at least one of said restrictions to modulate the pressures acting on said pressure responsive member to effect movement thereof as a function of the movement of said supported valve member, 'and-the force of said frictionless biasing means varying as a function of the movement of said supported valve member, whereby the movement of said supported valve member varies as a functionof engine speed to eifect corresponding movement of said control means also as a function of engine'speed. a

21. The combination of elements defined in claim 17, wherein said swingable means comprises at least one leaf spring member, each leaf spring member having only one fixed support in substantially its own plane, variable force second biasing means acting on said pressure responsive member to oppose the forces produced thereon by fluid pressures in 'said fluid circuit acting on "said pressure responsive member, the force of said lastnamed biasing means varying as a function of the moverr'i'e'ut of said pressure responsive member, said. valve means controlling pressures on onlytone side of said pressure-responsive member, the configuration. of said valve body member in relation to thesaid mating member adapted to produce modulated pressures .acting on said pressure responsive member to eifect. movementnthereof as a function of the movement of said, supported valve member, and the force of Said, frictionless biasing means varying as a function of the movement of .said supported valve member, whereby the movement of, said supported valve member varies as a function of engine speed to effect corresponding movement of said control means also as ,a function of engine speed.

22. In a governor for automatically controlling the speed of an engine comprising; in combination, control means to regulate 'the speed of the engine, afpre ssure responsive member connected .jto saidcontrol means for actuation thereof, afluid circuit havinga flow of iluid therethrough and communicating tvith ;s aid;pressu re responsive member. :valve means in saidfluid circuit for directing fluid therein. to ,saidipressure responsive rnemher to effect movement thereof, said valve means includirig a valve 'body-meinber andja mating member coop- ;erable therewith, two substantially parallel leaf spring face contact. 'of said supported .Yfilve member during said operational movements thereof, each of said leaf spring members having only one fixed support in substantially 'its own plane substantially frictionless movable sensingrneansf responsive, to changes in engine speed ahd acting on said supported tvalve member to effect movements thereofgfor producing movements of said pressure responsive member fandthereby amplifiedfforces acting on said control means,.;substantially ,fri c,t ionless biasing means opposing the forces produced by said sensing means, j'wher'eby, the, combined movements of said supported valve member, said movable sensing means, and said biasing means aresubstantiallyfrictionless and thereby respond substantially instantaneously and ciinsistently to minute changes in they forces produced by changes in bnginespeed, acting on said sensing means "to effect speed-controlling movements of said control 'me'ansifor maintaining within a predetermined variation a desired value of engine speed. 1 4 I A 23. he fluid mechanism having a stationarypart'and a pressure fluid circuit therein, valve means in said fluid circuit for controlling pressures therein, said valve means including a seating member and a valve body member, a leaf spring member acting to support one of said. valve members for substantially frictionless movements in a direction transverse to the plane of said leaf spring meniber and to prevent surface contact of said supported valve meinber during operationalnmo've'ments thereof, threaded fastening means including a head means to secure said leaf spring member to said stationary part, an antito'rque member between said head means and said leaf spring member and cooperating with said stationary part to prevent the torque 'of said head means from acting on said leaf springmember when said fastening means is. tightened, wherebyonly thrust forcesare applied to'said leaf spring member to maintainalignment of said supported valve member in relation to the other of said 'valve'm'embers. a 7 7 c 24. In a fluid mechanism having a stationary part and a pressure fluid. circuit therein, valve means including two orifice members in series in said circuit, said valve means also including two valvemembers connected together to modulate simultaneously the aperture of each of said or'ificeinembers, respectively, for controlling fluid pressure in said circuit between said two orifice member's, one of said valvemembers increasing the aperture of its said cooperating orifice member while the other of saidvalve members decreases 'the aperture of its said cooperating orificemember, two spaced substantially parallel swingabl'e leaf spring members having width fimpartin'g rigidity in one direction acting to support said valve members for substantially frictionless movements in a direction transverse ,to said first, named-direction and to suspend said valve vmembers within the fluid controlled the-rebywith only fluidcontact at the flow con trolling surfaces thereof :during operational movements; each of said leaf spring members having separate threaded fastening means including a head means to se'curesaid leaf spring member to said stationary part of said device, each "of said leaf spring members including aperture means "to produce sufficient clearance relative to said fastening means for self-aligning seating ofsaid respective snpportedvalve member in relation to the said corresponding orifice member'when said fastening means is tightened, ;-an a-ntitorque member between said head ,mean's and each of said {leaf spring members-and =cooperating with said stationary part to prevent the torque of said ;head means from acting on saidrespecti-ve leaf spring member as said head means is drawn tight to fasten said leaf spring member in adjusted position, whereby only *thr ust forces are-applied tofeach of said leaf spring members to maintain alignment of said sup- ;ported valve members in relation to the corresponding orificemembers. r v

25. In a fluid mechanism 'having a stationary part-and a pressure fluid circuit therein, valve'means in said fluid circuit 'for controlling pressures therein, said valve means including --a seating memberand a valve body member, =a-1eaf spring member acting to support-one of said valve members for substantially frictionless movements in a direction transverse to the plane of said-leaf spring memher and to prevent surface contact of -'-said supported :valve member during operational ,movements thereof, threaded .-fastening means including -a head means to secure 'said leaf spring member to-said stationary part, said leaf. spring member having sufficient clearance Irelative to said fastening means for self-alignment seating of said supportedvalve-member.in relation to the other of said valve members when said fastening means is tightened, ananti-torque member betweensaid head means and said leaf springrnember and cooperating with said stationary part topreve'ntthe torque of said head means from acting'onsaid leaf spring member whenIsaid fasteningpm'ea'n s is ftightehe'd, fwhereby only thrust forces are applied "to "said deaf spring'member "'t'o 'rnaintain alignment of said supported valve member in relation to the other of said valve members.

26. In a fluid mechanism having a stationary part and a pressure fluid circuit therein, valve means in said fluid circuit for controlling pressures therein, said valve means including a seating member and a valve body member, a leaf spring member acting to support one of said valve members for substantially frictionless movements in a direction transverse to the plane of said leaf spring member and to prevent surface contact of said supported valve member during operational movements thereof, fastening means to secure said leaf spring member between said stationary part and said fastening means, one of said valve members having a diverging valve face contour and being disposed in relation to the other of said valve members for guiding said supported valve member into self-alignment seating relationship with the other of said valve members before said fastening means is tightened, and said leaf spring member having means to provide suflicient clearance relative to said fastening means to facilitate said self-alignment seating of said supported valve member in relation to the other of said valve members when said fastening means is tightened.

27. The combination of means defined in claim 14, and

fastening means to secure said swingable means between a stationary part in said mechanism and said fastening means, and means to effect self-alignment seating of said supported valve member in relation to the other of said valve members when said fastening means is tightened.

28. The combination of elements defined in claim 14, and said fluid circuit including at least two restrictions, said pressure responsive member communicating with said circuit at a point between said two restrictions, said supported valve member varying the restrictive effect of at least one of said restrictions to modulate the pressures acting on said pressure responsive member, and fastening means to secure said leaf spring member between a stationary part in said mechanism and said fastening means, one of said valve members having a diverging valve face contour and being disposed in relation to the other said valve member for guiding said supported valve member into said self aligning seating relationship with said non-supported valve member before said fastening means is tightened, and said leaf spring member being disposed to provide suflicient clearance relative to said fastening means to facilitate self-alignment seating of said supported valve member in relation to said nonsupported valve member when said fastening means is tightened.

29. The combination of means defined in claim 17, and said swingable means includes a leaf spring member, and threaded fastening means including a head means to secure said leaf spring member to a stationary part in said governor, said leaf spring member having sufficient clearance relative to said fastening means for self-alignment seating of said supported valve member in relation to the said non-supported valve member when said fastenmg means is tightened, and one of said valve members having a diverging valve face contour and being dis osed m relation to the other of said valve members for guiding said supported valve member into said self-aligning seatmg relationship with said non-supported valve member before said fastening means is tightened, and the said other of said valve members being contoured to produce substantially a line contact in relation to said valve memher having a diverging face upon the seating thereof, and said valve means including a second similarly arranged valve body member cooperating with a similarly arranged second mating member, a second leaf spring member disposed substantially parallel to said first leaf spring member for supporting one of said second valve members, said two supported valve members being connected together for simultaneous movements to increase the aper ture between the said first mating member and said first valve body member while simultaneously decreasing the aperture between said second mating member and said second valve body member, and second similarly arranged fastening means, and said second leaf spring member having sufficient clearance for self-alignment seating'of said second supported valve member, one of said second valve members having a similarly diverging valve face contour and the other of said second valve members being similarly contoured to provide substantially line contact seating thereof, and said pressure responsive member com-- municating with said fluid circuit at a point between saidtwo non-supported valve members,

30. The combination of means defined in claim 17, in' which said engine includes an intake passage for the flow of air therethrough, and said fluid circuit communicateswith said intake passage for etfecting a flow of air through said circuit, said air circuit including at least two re-- strictions formed by said valve means, said first pressure responsive member communicating with said circuit at a" point between said two restrictions, said supported valve member varying simultaneously the restrictive effect of both of said restrictions for modulating the pressures acting on said pressure responsive member between the value of pressure at the inlet of said circuit to the value of pressure at the outlet of said circuit.

31. The combination of means defined in claim 1, and variable force second biasing means acting on said first pressure responsive member to oppose the forces produced thereon by fluid pressure in said fluid circuit acting on said first pressure responsive member, the force of said second biasing means varying as a function of the movement of said first pressure responsive member, said valve means being disposed to control pressures on only one side of said first pressure responsive members, the configuration of said valve means being disposed to produce modulated pressures acting on said first pressure responsive member to effect movement thereof as a function of the movement of said valve means, and the force of said frictionless biasing means varying as a function of the movement of said valve means, whereby the movement of said valve means varies as a function of engine speed to effect corresponding movement of said control means also as a function of engine speed.

32. The combination of means defined in claim 24, and one of said supported valve members and its cooperable orifice member being so arranged in relation to each other that at least one of said last-named two members includes a diverging valve face contour and being disposed in relation to the other of said last-named two members for guiding said supported valve member into selfalignment seating relationship with said corresponding orifice member before said corresponding fastening means is tightened, and the second supported valve member and its corresponding orifice member being similarly arranged to provide self-aligning seating thereof.

33. In a governor for automatically controlling the speed of a rotating machine, comprising in combination, control means to regulate the speed of the machine, a pressure responsive member connected to said control means for actuation thereof, a fluid circuit having a flow of fluid therethrough and communicating with said pressure responsive member, valve means in said fluid circuit for directing fluid therein to said pressure responsive member to etfect speed-controlling movements of said control means to maintain the speed of said machine, sensing means responsive to changes in the speed of said machine connected to said valve means for effecting movement thereof, and leaf spring means having width imparting rigidity in the direction of its own plane connected to said valve means to support same for substantially frictionless movements in a direction transverse to said first direction and for frictionless suspension within the fluid controlled thereby with only fluid contact at the flow controlling surfaces of said valve means during operational sage for the flow of air therethrough, said engine including means causing the pressure of at least a portion of said intake-passage-air to vary as a function of engine speed, control means to regulate engine speed, the combination of a fluid device connected to said control means for actuation thereof, said device including a pressureresponsive member communicating with said speed-varying intake-passage air-pressure for effecting movements thereof in response to speed-effected changes in said air pressure to produce speed-controlling movements of said control means, a sealed expansible member movable in response to changes in the absolute value of substantially atmospheric air pressure disposed to control forces acting on said pressure responsive member to compensate for undesirable changes in said speed-varying air pressure acting thereon produced by changes in the density of said air flowing through said intake passage as the altitude is changed.

35. In a governor for an engine having an intake passage for the flow of air therethrough, said engine including means causing the pressure of at least a portion of said intake-passage-air to vary as a function of engine speed, control means to regulate engine speed, the combination of means to effect speed-regulating movements of said control means comprising, a pressure responsive member connected to said control means for actuation thereof, a fluid circuit having a flow of fluid therethrough and communicating with said pressure responsive member, valve means in said circuit to control pressure therein acting on said pressure responsive member to effect speedcontrolling movements of said control means, a second pressure responsive member connected to said valve means for actuation thereof, said second pressure responsive member communicating with said speed-varying intakepassage air-pressure for effecting movements thereof in response to changes in engine speed, an expansible member having a sealed reference chamber on one side thereof with the other side thereof being exposed to a region of air pressure corresponding to substantially atmospheric pressure to effect movements of said expansible member as a function of changes in the absolute value of said region-air-pressure, said expansible member being so arranged in relation to said valve means that said movements of said expansible member produces forces varying as a function of said absolute value of said region-airpressure to affect operation of said valve means to compensate for undesirable changes in said speed-varying intake-passage air-pressure acting on said second pressure responsive member produced by changes in the density of said air flowing through said intake passage as the altitude is changed.

36. In a governor for controlling the speed of an engine having an intake passage for the flow of air therethrough, said engine including means causing the pressure of at least a portion of said intake-passage-air to vary as a function of engine speed, control means to regulate engine speed, a pressure responsive member connected to said control means for actuation thereof, a fluid circuit having a flow of fluid therethrough and communicating with said pressure responsive member, valve means in said fluid circuit for directing fluid therein to said pressure responsive member to eifect movement thereof, said valve means including a valve body member and a mating member cooperable therewith, substantially frictionless swingable means disposed to impart rigidity in one direction acting to support one of said valve members for substantially frictionless movements in a direction transverse to said first-named direction and to prevent surface contact of said supported valve member during said operational movements thereof, a second pressure responsive member connected to said supported valve member for actuation thereof, biasing means opposing the forces produced by said second pressure responsive member, said second pressure responsive member communicating with said speed-varying intake-passage air-pressure for effecting movements thereof and cooperating said supported valve member in response to changes in engine speed to produce speed-controlling movements of said first-named pressure responsive member and cooperable control means.

37. In a governor for controlling the speed of an engine including means to control the speed of the engine and means driven by the engine and rotating as a function of engine speed to blow air, the combination of means to effect speed-controlling movements of said control means comprising, a pressure responsive member connected to said control means for actuation thereof, a fluid circuit having a flow of fluid therethrough and communicating with said pressure responsive member, valve means in said fluid circuit for directing fluid therein to said pressure responsive member to effect movement thereof, said valve means including a valve body member and a mating member cooperable therewith, substantially frictionless swingable means disposed to impart rigidity in one direction acting to support one of said valve members for substantially frictionless movements in a direction transverse to said first-named direction and to prevent surface contact of said supported valve member during said operational movements thereof, a second pressure responsive member connected to said supported valve member for actuation thereof, biasing means opposing the forces produced by said second pressure responsive member, means connecting said second pressure responsive member with airblown by said air blowing means to produce a pneumatic pressure acting on said second pressure responsive member varying as a function of engine speed for effecting movements thereof and of said supported valve member in response to changes in engine speed to produce said speed-controlling movements of said first-named pressure responsive member and cooperable control means.

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